Lubricant distribution system with overfill protection

Abstract

A lubricant distribution system for supplying lubricant. The system comprises a lubricant reservoir and a pump assembly for pumping the lubricant. The pump assembly includes a crankcase with a crank assembly that can be inserted into and removed from the crankcase housing without disassembling the crank assembly, thus facilitating crankcase assembly and disassembly. The system also includes a shut-off valve that stops the reservoir from being filled with lubricant. The shut-off valve includes a blocker that prevents lubricant flow to the reservoir and an actuating surface that allows the blocker to be positioned to prevent lubricant flow. To prevent overfilling, the actuating surface is movable relative to the blocker. The system also includes a bracket with a one-way valve mounted on it.The one-way valve can be removed from the holder for easy replacement or cleaning.

Description

AREA

[0001] The present disclosure relates to lubricant distribution systems and, more particularly, to an overfill prevention device for a lubricant reservoir. BACKGROUND

[0002] Lubricant distribution systems deliver lubricant (e.g., grease) to one or more lubrication points. Typically, lubricant distribution systems include a pump, such as those shown in the following U.S. patents: 2,187,684; 2,636,441; 2,787,225; 3,469,532; 3,502,029; 3,945,772; 4,487,340; 4,762,474; and 6,102,676, which serves to pump lubricant from a reservoir. In one type of lubrication system, called a single-line injector lubrication system, the lubricant distribution system pumps lubricant through a single supply line (may include one or more individual supply lines) to one or more injectors, which deliver metered amounts of lubricant to the lubrication points. SUMMARY

[0003] In one aspect, a lubricant distribution system includes a reservoir configured to contain lubricant. The reservoir includes a follower plate configured to move up and down within the reservoir in response to a changing lubricant level within the reservoir. A reservoir inlet is positioned to deliver lubricant to the reservoir. A shut-off valve is in fluid communication with the reservoir inlet. The shut-off valve includes a blocker selectively positionable to permit and prevent lubricant flow through the reservoir inlet.The shut-off valve includes a valve actuator with a follower plate engagement surface arranged to engage the follower plate when the lubricant in the reservoir fills to a predetermined level to position the blocker to prevent lubricant flow through the reservoir inlet. The follower plate engagement surface is movable relative to the blocker.

[0004] In another aspect, a lubricant shut-off valve comprises a valve housing having an inlet, an outlet, and a passageway fluidly connecting the inlet and the outlet. A blocker is selectively positionable relative to the valve housing to permit lubricant flow through the passageway from the inlet to the outlet and to prevent lubricant flow through the passageway from the inlet to the outlet. A valve actuator is operatively connected to the blocker to selectively position the blocker relative to the valve housing. The valve actuator has an actuating surface configured to be movable to move the blocker to a position where the blocker prevents lubricant flow through the passageway. The actuating surface is movable relative to the blocker.

[0005] Further tasks and features will be partly obvious and partly highlighted below. BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a perspective view of a lubricant distribution system according to an embodiment of the present disclosure, with a wall of a reservoir shown transparent to show internal details; Fig. 2 is a cross-section of the lubricant distribution system; Fig. 3 is an enlarged, fragmentary, perspective front view of the lubricant distribution system; Fig. 4 is an enlarged, fragmentary, perspective rear view of the lubricant distribution system; Fig. 5A is a cross-sectional view of a shut-off valve of the lubricant distribution system according to an embodiment of the present disclosure, wherein the shut-off valve is in an open configuration; Fig. 5B is a cross-sectional view of the shut-off valve with the shut-off valve in a closed configuration; Fig. 5C is a cross-sectional view of the shut-off valve with the shut-off valve in another closed configuration; Fig. 5D is a cross-sectional view of the shut-off valve with the shut-off valve in another closed configuration; Fig. 6 is a partially exploded view of a pump assembly of the lubricant distribution system according to an embodiment of the present disclosure, the pump assembly including an electric motor; Fig. 7 is a perspective view of a portion of a pump assembly according to another embodiment of the present disclosure, the pump assembly including a hydraulic motor; Fig. Figure 8 is a cross-section of a crankcase and an electric motor of the pump assembly of Fig. 6; Fig. 9 is an exploded view of the crankcase; Fig. 10 is a perspective view of a crankcase housing; Fig. 11 is an enlarged view of the pump assembly of Fig. 6; Fig. 12 is a rear perspective view of a valve assembly of the lubricant distribution system according to an embodiment of the present disclosure, the valve assembly including an electrically operated vent valve; Fig. 13 is a front perspective view of the valve assembly; Fig. 14 is a cross-section of the valve assembly taken along line 14-14 of Fig. 12; Fig. 15 is a cross-section of the valve assembly taken along line 15-15 of Fig. 12; Fig. 16 is a cross-section of the valve assembly taken along line 16-16 of Fig. 13; Fig. 17 is a perspective view of a mounting bracket of the valve assembly; Fig. 18 is a schematic view of the valve arrangement; Fig. 19 is a perspective view of a valve assembly according to another embodiment of the present disclosure, the valve assembly including a hydraulically actuated vent valve; Fig. 20 is a perspective view of the hydraulically operated vent valve; Fig. 21A is a cross-sectional view of the hydraulically actuated vent valve, wherein the hydraulically actuated vent valve is in an open or venting configuration; and Fig. 21B is a cross-sectional view of the hydraulically actuated vent valve, wherein the hydraulically actuated vent valve is in a closed or non-venting configuration.

[0006] In all drawings, corresponding reference symbols designate corresponding parts. DETAILED DESCRIPTION

[0007] With reference to the Fig. 1 and Fig. 2, one embodiment of a lubricant distribution system according to the present disclosure is generally designated by reference numeral 10. The lubricant distribution system 10 of the present disclosure is suitable for supplying or sending lubricant, such as grease, to one or more lubrication points (not shown). These lubrication points may be part of a machine (not shown), such as a factory plant or a large construction vehicle, or any other device requiring lubrication.The lubricant distribution system 10 may be part of an overall lubrication system, such as a single-line injector lubrication system, including the lubricant distribution system of the present disclosure, one or more injectors (in the broadest sense, lubricant metering devices) that deliver lubricant to the lubrication points, and one or more individual supply lines that transport lubricant from the lubricant distribution system to the one or more injectors. Although the description refers to a single-line injector lubrication system, it is understood that aspects of the present disclosure may also be implemented in other types of lubrication systems and in environments other than lubrication.Furthermore, while the system 10 of the present disclosure is described in the context of delivering lubricant, it may also be used to deliver other types of fluids, such as inks, friction modifiers, and mastics / adhesives. The use of the term "lubricant" herein is intended to encompass such other types of fluids.

[0008] The lubricant distribution system 10 includes a reservoir or drum 12 and a pump assembly 14 supported by the reservoir. The reservoir 12 is configured to contain the lubricant to be dispensed by the lubricant distribution system 10. The reservoir 12 includes a base or bottom plate, a cylindrical sidewall 18, and a lid or top plate 20 defining an interior space 22 containing the lubricant. The pump assembly 14 is mounted to the lid 20, such as with one or more fasteners. The reservoir 12 includes a follower plate 24, as is well known in the art. The follower plate 24 is configured to move up and down within the reservoir in response to a changing lubricant level within the reservoir 12.The follower plate 24 bears against the lubricant contained in the reservoir 12 and moves up and down with the lubricant level in the reservoir. The follower plate 24 can pressurize the lubricant in the reservoir and can also scrape lubricant from the inner surface of the sidewall 18 as the lubricant level drops (as lubricant is pumped from the reservoir by the pump assembly 14). The follower plate 24 can slidably and sealingly engage the sidewall 18 and the pump assembly 14. In one embodiment, the follower plate 24 can comprise a foam insert mounted to a metal plate. It is understood that other configurations and constructions of the follower plate are within the scope of the present disclosure.A vent valve (not shown) may be provided on the lid 20 of the reservoir 12 to relieve the pressure in the interior space 22 as the follower plate 24 moves up and down in the reservoir.

[0009] The pump assembly 14 includes a motor 26, a pump 28, and a drive train 30 operatively connecting the motor to the pump. The pump 28 is configured to pump lubricant from the reservoir 12. In the illustrated embodiment, the pump 28 is a lance pump. Examples of lance pumps are shown and described in U.S. Pat. Nos. 9,239,044 and 6,102,676, which are hereby incorporated by reference in their entirety. The pump 28 includes a lance structure 32 that extends through a hole in the lid 20 downward into the interior 22 of the reservoir 12 toward the base 16. It is understood that the use of pump types other than lance pumps is within the scope of the present disclosure.

[0010] The lubricant distribution system 10 includes a reservoir supply or refill inlet 34 configured to supply lubricant to the reservoir 12 to refill the reservoir with lubricant after the lubricant is depleted. When the amount of lubricant in the reservoir 12 is depleted, the reservoir must be refilled with lubricant. The reservoir 12 is refilled by a lubricant supply (not shown). Often, the lubricant supply is located some distance from the reservoir 12. For example, the reservoir 12 may be located inside a building, and the lubricant supply may be located in a truck outside the building. The interior 22 of the reservoir 12 is filled with lubricant, which is pumped from the lubricant supply to the reservoir refill inlet 34.The reservoir refill inlet 34 is provided near the base 16 of the reservoir 12, below the follower plate 24. In the illustrated embodiment, the reservoir refill inlet 34 is formed by the pump 28 (e.g., a portion of the pump 28), although other configurations are within the scope of the present disclosure. For example, the reservoir refill inlet may be a portion of the reservoir 12, provided, for example, in the sidewall 18, or the reservoir refill inlet may be provided by a separate structure, such as a conduit extending downward from the lid 20 and through the follower plate 24, or may be part of the follower plate. In the illustrated embodiment, the pump 28 includes a pump refill inlet 36 (Fig. Fig. 11) and a pump refill passage 38 (see general Fig. 2) that provides fluid communication between the pump refill inlet and the reservoir refill inlet 34. The pump refill passage 38 extends along the lance structure 32 of the pump 28 to the reservoir refill inlet 34. The lubricant is moved by the lubricant supply through the pump refill inlet 36, through the pump refill passage 38, and out of the reservoir refill inlet 34. In this manner, the reservoir refill inlet 34 can also be considered a pump refill inlet. In the illustrated embodiment, the reservoir refill inlet 34 includes one or more openings and / or an open lower end of the pump refill passage 38. Other configurations of the reservoir refill inlet 34 are also within the scope of the present disclosure.

[0011] The lubricant is pumped out of the reservoir 12 by the pump 28. When the lubricant contained in the reservoir 12 is used up, the reservoir is refilled by the lubricant supply, which pumps lubricant to the reservoir refill inlet 34. With reference to Fig. 3 and Fig. 4, the lubricant distribution system 10 includes a shut-off valve 40 for the lubricant. The shut-off valve 40 is configured to stop the flow of lubricant from the lubricant supply into the interior 22 of the reservoir 12 when the reservoir is sufficiently filled with lubricant, i.e., when the lubricant reaches the predetermined fill level. The shut-off valve 40 is mounted on the cover 20 of the reservoir 12. The shut-off valve 40 is in fluid communication with the reservoir refill inlet 34. The shut-off valve 40 is fluidly arranged between the lubricant supply and the reservoir refill inlet 34 to selectively permit or prevent the flow of lubricant from the lubricant supply to the reservoir refill inlet 34.

[0012] With reference to Fig. 5A-D, the shut-off valve 40 includes a valve housing 42. The valve housing 42 may comprise one or more pieces coupled together. The valve housing 42 includes a shut-off valve inlet 44, a shut-off valve outlet 46, and a shut-off valve passage 48 fluidly connecting the shut-off valve inlet and the shut-off valve outlet. The shut-off valve inlet 44 is configured to receive lubricant from the lubricant supply. The shut-off valve inlet 44 may be configured to connect to a conduit system (not shown), such as a line, hose, fitting, etc., that transports the lubricant from the lubricant supply to the shut-off valve 40.In one embodiment, the isolation valve inlet 44 is connected to (e.g., fluidly downstream of) a separator (e.g., a hydraulic / grease separator) (not shown) that can quickly connect and disconnect the lubricant supply to the isolation valve 40. The separator can automatically close when not connected to the lubricant supply and automatically open when connected to the lubricant supply. The isolation valve outlet 46 is configured to connect to a refill line 50 (. Fig. 3 and Fig. 4) which transports the lubricant from the isolation valve 40 toward the reservoir refill inlet 34 (via the pump refill inlet 36 and the pump refill passage 38). The isolation valve 40 includes a blocker 52 that is selectively positionable relative to the valve housing to permit the flow of lubricant from the isolation valve inlet 44 to the isolation valve outlet 46 and to prevent or block the flow of lubricant from the isolation valve inlet to the isolation valve outlet. Because the isolation valve outlet 46 is in fluid communication with the reservoir refill inlet 34, permitting or preventing the flow of lubricant through the isolation valve 40 permits and prevents the flow of lubricant from the reservoir refill inlet 34 into the interior space 22 of the reservoir 12.The check valve passage 48 includes a blocker section 48A, and the blocker 52 is movably positioned within the blocker section. In the illustrated embodiment, the blocker 52 comprises a spool. The spool includes a sealing head 54, a guide head 56, and a stem 58 extending between the sealing and guide heads. The sealing head 54 is configured to engage (more precisely, sealingly engage) an inner sealing surface 60 of the valve housing 42 that defines a portion of the blocker section 48A. The inner sealing surface 60 and the sealing head 54 are each cylindrical, allowing the spool 58 to slide along the sealing surface while maintaining a seal between the spool and the valve housing 42.The guide head 56 also sealingly engages the valve body 42 and helps guide the movement of the spool within the blocker section 48A of the check valve passage 48. The spool includes a vent passage 62 that extends through the spool from one side of the spool to the other, thereby interconnecting the portions of the valve passage 48 on either side of the spool without interruptions or blockages. The vent passage 62 allows pressure to equalize on both sides of the spool within the valve passage 48 as the spool moves within the valve passage. Without the vent passage 62, pressure could build up on one side or the other of the spool within the valve passage 48, which could impede, if not prevent, the movement of the spool within the valve passage.Other configurations of the blocker are also within the scope of the present disclosure. Instead of a spool, the blocker may, for example, include a poppet that selectively engages a seat to permit or prevent the flow of lubricant.

[0013] The blocker 52 moves or slides linearly along a blocker axis BA to selectively permit or prevent the flow of lubricant. The blocker 52 is movable relative to the valve body 42 between an open position ( Fig. 5A) and several closed positions ( Fig. 5B-D) (generally speaking, at least one closed position). The blocker 52 moves along a blocker axis BA between the open and closed positions. In the Fig. 5A, the sealing head 54 of the blocker 52 is spaced from the inner sealing surface 60, thereby permitting the flow of lubricant between the valve housing 42 and the sealing head. In the open position, the lubricant can flow freely along the check valve passage 48 from the check valve inlet 44 to the check valve outlet 46. The lubricant flows along the check valve passage 48, around the stem 48 (which has a diameter smaller than the diameter of the blocker section 48A), around the sealing head 54, and toward the check valve outlet 46. In the closed positions ( Fig. 5B-D), the sealing head 54 of the blocker 52 engages the inner sealing surface 60, forming a circumferential seal between the sealing head 54 and the valve body 42, preventing the flow of lubricant therebetween, thereby preventing the flow of lubricant through the valve passage 48. Fig. Figure 5B shows the blocker 52 in a closed position, and Fig. 5CD show the blocker in a different closed position. Because the blocker 52 comprises a spool, the blocker can continue to move relative to the valve body 42 after the seal is formed. In other words, different portions of the seal head 54 can engage the inner sealing surface 60 to form the seal in different closed positions. This allows the blocker 52 to maintain the seal with the valve body 42 even as the blocker continues to move in a first or closing direction. The closing direction is the direction in which the blocker moves along the blocker axis BA from the open position toward the closed positions. In Fig. 5A-D, the closing direction is generally upward. The shutoff valve 40 includes an end stop 64 designed to be engaged by the blocker 52 (more specifically, the guide head 56) to limit the movement of the blocker in the closing direction. Fig. 5C-D illustrate the blocker 52 in engagement with the end stop 64, showing the most closed position in the blocker's closing direction. For reference, a second or opening direction is opposite the closing direction. The opening direction is the direction in which the blocker moves along the blocker axis BA from the closed positions toward the open position. Fig. 5A-D the opening direction is generally downward.

[0014] The shut-off valve 40 includes a blocker or return spring 66 that biases the blocker 52 toward the open position. In the illustrated embodiment, the blocker spring 66 comprises a coil spring having one end engaged with the end stop 64 and the other end engaged with the guide head 56. As the blocker 52 moves from the open position toward the closed position, the blocker compresses the blocker spring 66.

[0015] The shut-off valve 40 includes a valve actuator 68 operatively connected to the blocker 52 to selectively position or move the blocker relative to the valve housing 42. More specifically, the valve actuator 58 is configured to move the blocker 52 from the open position to the closed positions. The valve actuator 68 is configured to move along the blocker axis BA to position the blocker relative to the valve housing 42. In the illustrated embodiment, the valve actuator 58 includes a slider disposed within a bore 70 of the valve housing 42. The bore 70 is parallel or coextensive with the blocker axis BA. The slider is configured to slide (in the closing direction) within the bore relative to the valve housing 42 along the blocker axis BA to position or move the blocker to one of the closed positions.The valve actuator 58 includes an actuating or follower plate engagement surface 72. The actuating surface 72 is configured to be engaged and moved by the follower plate 24 when lubricant fills the reservoir 12 to a predetermined level to move the blocker 52 to one of the closed positions, thereby preventing the flow of lubricant through the shutoff valve 40. An upper end of the valve actuator 58 is configured to engage the blocker 52 and move the blocker from the open position toward the closed positions. The actuating surface 72 is defined by a lower end of the valve actuator 48 and is configured to be engaged and moved by the follower plate 24 as the follower plate moves upward within the reservoir 12 as the reservoir is refilled with lubricant.

[0016] To protect the shutoff valve 40 and other components (e.g., the follower plate 24) of the lubricant distribution system 10 from damage that may result from overfilling the reservoir 12 with lubricant, the shutoff valve 40 is equipped with overfill protection measures. Since the follower plate 24 continues to rise as the reservoir 12 is filled with lubricant, overfilling the reservoir 12 may cause the follower plate 24 to place excessive stress on the shutoff valve and / or other components of the lubricant distribution system.Although the follower plate 24 is described in the context of an overfill, the follower plate 24 may also rise above the predetermined fill level for other reasons, such as thermal expansion, leakage, improper filling, or otherwise, and the overfill protection measures described herein protect the lubricant distribution system 10 in these situations as well. One overfill protection measure includes the actuating surface 72 being movable relative to the blocker 52. This allows the actuating surface 72 to continue to be moved by the follower plate 24, such as when the follower plate continues to move upward due to overfill, even though the blocker 52 is engaged with the end stop 64 and is thereby prevented from further movement in the closing direction.This movement of the actuating surface 72 allows the follower plate 24 to move further upward without damaging or unduly stressing the lubricant distribution system 10. The actuating surface 72 is movable relative to the blocker 52 along the shutoff axis BA. The shutoff valve 40 includes an overfill spring 74 configured to allow the actuating surface 72 to move relative to the blocker 52. The overfill spring 74 is operatively disposed between the actuating surface 72 and the blocker 52 such that a force transmitted from the engagement of the follower plate with the actuating surface is transmitted through the overfill spring to the blocker. Thus, the overfill spring 74 is configured to bias the blocker 52 and the actuating surface 72 away from each other. In the illustrated embodiment, the valve actuator 68 (more precisely, the slider) includes the overfill spring 74.The valve actuator 68 (more precisely, the slider) includes a first or upper rod or valve stem 76 and a second or lower rod or valve stem 78. The first and second rods 76, 78 are supported by the valve housing 42 and are slidable relative thereto along the blocker axis BA. The first and second rods 76, 78 are also slidable relative to each other along the blocker axis BA. The first rod 76 is configured to engage and slide the blocker 52. The second rod 78 includes the actuating surface 72. The second rod 78 may also include a lip or shoulder 80 configured to engage a lip or shoulder 82 of the valve housing 42 within the bore to prevent the second rod 78, and hence the valve actuator 68, from falling out of the bore in the opening direction.The overfill spring 74 is designed to allow the first and second rods to slide relative to each other. The overfill spring 74 is disposed between the first and second rods 76, 78. The overfill spring 74 is also supported by the valve body and is slidable relative thereto along the blocker axis BA. Together, the first and second rods 76, 78 and the overfill spring 74 can slide together within the bore 70 when the follower plate 24 engages the actuating surface 72 and lifts it upward to move the blocker 52 to one of the closed positions. Then, the second rod 78 can move further relative to the first rod, if necessary, compressing the overfill spring 74 if the follower plate 24 rises above the predetermined fill level.

[0017] Another overfill protection measure of the shut-off valve 40 is the blocker 52 itself. Since the blocker 52 comprises a control spool and can be moved into several different closed positions, as described above, the blocker also provides overfill protection. For example, even if the blocker 52 is in the Fig. 5B (where the sealing head 54 just sealingly engages the inner sealing surface 60), continue to move in the closing direction (to other closed positions) against the force of the blocker spring 66, thereby allowing the follower plate 24 to move further upward within the reservoir 12 without damaging or unduly stressing the lubricant distribution system 10 or its components. After the blocker 52 moves to the position shown in Fig. 5C-D, where the blocker 52 is prevented from further movement in the closing direction due to the end stop 64, the overfill spring 74 is then used to provide further overfill protection.

[0018] Together, the locking spring 66 and the overfill spring 74 resist the follower plate 24 from rising above the predetermined fill level (where the predetermined fill level is the lubricant level when the follower plate 24 has just moved the blocker 52 into the initial closed position). To ensure that the shut-off valve 40 operates properly, the spring constant of the overfill spring 74 is greater (e.g., 2 times, 3 times, 4 times, 5 times, etc.) than the spring constant of the blocker spring 66. As a result, the blocker spring 66 compresses before the overfill spring 74. This ensures that the blocker 52 is moved to one of the closed positions before the overfill spring 74 begins to compress.In other words, this ensures that the blocker 52 is moved to one of the closed positions before the actuating surface 72 begins to move relative to the blocker. When the blocker 52 is in the position shown in . Fig. 5A, the overfill spring 74 is generally not compressed (any compression of the overfill spring due to the weight of the first rod 76 and the force from the blocker spring 66 is negligible). When the blocker 52 is in the position shown in Fig. 5B, the overfill spring 74 is also generally not compressed. When the shut-off valve 40 is in the position shown in Fig. 5C, the blocker 52 is in the configuration shown in Fig. 5C (which is different from the initial closed position). In this embodiment, the overfill spring 74 is still not compressed, and the follower plate 24 has moved the valve actuator 68 just enough to push the blocker 52 into engagement with the end stop 64. Because the blocker 52 is prevented from further movement in the closing direction, further upward movement of the follower plate 24 moves the actuating surface 72 relative to the blocker, thereby compressing the overfill spring 74. The follower plate 24 can continue to compress the overfill spring 74 until the actuating surface 72 is flush with a lower end of the valve housing 42, as shown in Fig. 5D. Accordingly, Fig. 5A-D generally show the progression of the shut-off valve during a refilling operation, with the blocker 52 starting in an open position ( Fig. 5A), the blocker moves to the initial closed position ( Fig. 5B), the blocker moves to the most closed position ( Fig. 5C, if this is required for initial overfill protection), and then the actuating surface 72 moves relative to the blocker ( Fig. 5D if required for additional overcrowding protection).

[0019] The refill operation of the lubricant distribution system 10 will now be described. When the lubricant level in the reservoir 12 is below the predetermined fill level (e.g., because the reservoir is empty), the follower plate 24 is spaced from the actuating surface 72, and the blocker 52 is in the open position (due to the blocker spring 66). The lubricant from the lubricant supply thereby flows through the shut-off valve 40 toward the reservoir refill inlet 34 and into the reservoir 12. As the interior 22 of the reservoir 12 is refilled with lubricant, the follower plate 24 is lifted upward. When the lubricant in the reservoir 12 has almost reached the predetermined fill level, the follower plate 24 contacts the actuating surface 72 and pushes the valve actuator 68 upward in the closing direction.As the valve actuator 68 rises upward, the valve actuator pushes the blocker 52 in the closing direction to one of the closed positions. In this closed position, the blocker 52 prevents additional lubrication from flowing through the isolation valve 40 and into the reservoir 12. Should the follower disc 24 continue to rise within the reservoir 12 due to overfill, thermal expansion, leakage, improper filling, or any other reason, the blocker 52 continues to move in the closing direction, further compressing the blocker spring 66. This provides primary or preliminary overfill protection. Should the follower disc 24 continue to rise within the reservoir 12 after the blocker 52 contacts the end stop 64, the follower disc is able to rise further by compressing the overfill spring 74. This provides secondary or secondary overfill protection.The follower plate 24 can continue to rise and compress the overfill spring 74 until the actuating surface 72 is flush with the lower end of the valve body 74 (. Fig. 5D). It will be appreciated that in embodiments where the blocker does not include a spool, the protection provided by the overfill spring may be the initial (and possibly only) form of overfill protection.

[0020] With reference to Fig. 3 and Fig. 4 on Fig. 6-10, the pump assembly 14 will now be described in more detail. The pump assembly 14 is configured to pump the lubricant from the reservoir 12. As mentioned above, the pump assembly 14 includes the motor 26, the pump 28, and the drive train 30. The motor 26 has an output shaft 86 configured to rotate about a rotational axis AR ( Fig. 8) to drive operation of pump 28. Drivetrain 30 connects engine 26 to pump 28 such that operation of the engine operates the pump to pump lubricant from reservoir 12. In the illustrated embodiment, drivetrain 30 includes a crankcase 100. Crankcase 100 operatively connects engine 26 to pump 28. In other embodiments, drivetrain 30 may include one or more additional components (e.g., rods, shafts, linkages, etc.) that operatively connect the engine to the pump.

[0021] The crankcase 100 includes a housing 102 and a crank or crank assembly 104 disposed within the housing (an interior thereof). The crank assembly 104 is configured to convert rotary motion from the engine 26 (more specifically, the rotation of the output shaft 86) into linear motion for the pump 28. Referring to Fig. 6, the pump 28 includes a pump rod 84 (broadly defined, a pump link) that moves up and down (broadly reciprocating) to operate the pump and pump the lubricant from the reservoir 12. The pump rod 84 is connected to the drive train 30, more specifically, to the crank assembly 104 of the crankcase 100, to drive the pump rod (up and down) to operate the pump. Accordingly, the crank assembly 104 converts the rotary motion from the motor 26 into linear motion to drive linear (e.g., up and down) motion of the pump rod 84 to pump lubricant from the reservoir 12.

[0022] With reference to Fig. 8 and Fig. 9, the crank assembly 104 includes a crankshaft 106, a piston or slider 108, and a connecting rod 110. The connecting rod 110 interconnects the crankshaft 106 and the piston 108. The crankshaft 106 includes a drive pulley 112, an idler or follower pulley 114, and a crankpin or crankshaft 116. The crankpin 116 extends between the drive pulley 112 and the idler pulley 114. The crankpin 116 is connected to the drive pulley 112 via a connection 118. Preferably, the connection 118 between the crankpin 116 and the drive pulley 112 is a fixed connection such that the crankpin and the drive pulley are fixed relative to each other (e.g., do not move relative to each other).In one embodiment, the connection 118 between the crankpin 116 and the drive pulley 112 is an interference fit (the end of the crankpin is pressed into the drive pulley), although other connections, such as welding, fasteners, integral molding, etc., are within the scope of the present disclosure. The drive pulley 112 is driven or rotated by (e.g., directly by) the engine 26. It is preferable to fix the connection 118 between the crankpin 116 and the drive pulley 112, as it provides a stronger and more permanent transfer of rotational force from the drive pulley to the crankpin and, thus, to the rest of the crankshaft 106. This results in the connection 118 between the crankpin 116 and the drive pulley 112 being capable of having a longer service life.The drive pulley 112 includes a motor connector 120 for operatively connecting the motor 26 to the crankshaft 106. The motor connector 120 is configured to be connected (e.g., directly connected) to the motor 26 such that the motor drives rotation of the drive pulley 112 and, thus, the crankshaft 106. In the illustrated embodiment, the motor connector 120 is directly connected to the output shaft 86 of the motor 26, although in other embodiments, one or more intermediate components may connect the motor connector to the output shaft. In one embodiment, the motor connector 120 includes a keyed opening, and the output shaft 86 has keyways configured to mate with the keyways of the opening, although other ways of connecting the output shaft and the drive pulley 112 to each other are within the scope of the present disclosure.The crankpin 116 is connected to the idler pulley 114 via a connection 122. Preferably, the connection 122 between the crankpin 116 and the idler pulley 114 allows the crankpin and the idler pulley to rotate relative to each other. In one embodiment, the connection 122 between the crankpin 116 and the idler pulley 114 is a sliding fit connection, although other types of rotary connections, such as fasteners, are within the scope of the present disclosure. Accordingly, the drive pulley 112 and the idler pulley 114 are capable of rotating or pivoting relative to each other due to the connection 122.This relative rotation between the drive pulley 112 and the idler pulley 114 simplifies the assembly of the crankshaft 106 by eliminating the need to concentrically align the drive and idler pulleys during assembly, as would be the case if the drive and idler pulleys were fixed relative to each other.

[0023] The connecting rod 110 is mounted on or coupled to the crankpin 116 of the crankshaft 106. The crankpin 116 extends through an opening at one end of the connecting rod 110. A bearing 124 is disposed between the crankpin 116 and the connecting rod 110 to allow the crankpin and connecting rod to rotate relative to each other. In the illustrated embodiment, the crankshaft 106 includes spacers 128 disposed on the crankpin 116 to position (more accurately, center) the connecting rod 110 (and the bearing 124) on the crankpin between the drive and idler pulleys 112, 114. The other end of the connecting rod 110 is connected to the piston 108. The piston 108 includes a wrist pin or piston shaft 126. The connecting rod 110 is mounted on or coupled to the piston pin 126.The piston pin 126 extends through an opening at the other end of the connecting rod 110. A bearing 124 is disposed between the piston pin 126 and the connecting rod 110 to allow the piston pin and the connecting rod to rotate relative to each other.

[0024] The piston 108 is arranged in a liner 130 and moves linearly back and forth within the liner along a piston axis PA while the crankshaft 106 rotates. The liner 130 is cylindrical. Preferably, the liner 130 protrudes from a lower end of the housing 102. The protruding end of the liner 130 is adapted to pass through a corresponding recess or opening 88 ( Fig. 6) to be received in a pump housing 96 of the pump 28. In this manner, the bushing 130 acts as a guide designed to engage the pump 28 to align the pump and the crankcase 100 relative to each other. This maintains concentricity and ensures that the piston 108 and the pump rod 84 are aligned when the crankcase 100 and the pump 28 are coupled together. The pump rod 84 projects upwardly from the recess 88 of the pump housing 96. The pump rod 84 of the pump 28 is connected to the piston 108. Accordingly, the piston 108 drives the linear reciprocating movement of the pump rod 84 to pump the lubricant from the reservoir 12. In the illustrated embodiment, the pump rod 84 is connected to the piston 108 (generally the crank assembly 104) via a sliding connection 132.In the illustrated embodiment, the sliding connection 132 includes a T-slot 134. The upper end of the pump rod 84 has a flange disposed above a circumferential groove, sliding into the T-slot 134, and thereby connecting the pump rod 84 to the piston 108. The sliding connection 132 allows the pump rod 84 to be connected to the crank assembly 104 quickly and easily, in contrast to, for example, a threaded connection, which requires numerous turns and can be cumbersome and time-consuming. The pump rod 84 slides in and out of the T-slot 134 along an axis. In the illustrated embodiment, the orientation of the piston 108 is such that the axis is generally parallel to the rotational axis AR. It should be understood, however, that the axis (generally the orientation of the T-slot 134) may have any orientation that lies within a plane normal to the piston axis PA.The sliding connection 132 also allows the piston 108 and the pump rod 84 to rotate relative to each other. This, in combination with the protruding end of the bushing 130 being received by the recess 88 in the pump housing 96 (which also allows rotation between the crankcase 100 and the pump 28), allows the crankcase 100 to be rotated into several different orientations relative to the pump 28. This allows the user to select the desired orientation of the crankcase 100 and the motor 26 relative to the pump 28. The user can orient the crankcase 100 and the motor 26 to avoid interference with other components, such as components of the equipment to which the lubricant distribution system 10 is mounted.In the illustrated embodiment, the housing 102 of the crankcase 100 is secured to the pump housing 96 of the pump 28 with four (broadly speaking, one or more) fasteners. The openings that receive the fasteners in the housing 102 and the pump housing 96 are arranged so that the crankcase 100 can be secured to the pump 28 in one of four different orientations, each spaced 90 degrees apart (about the piston axis PA). In each of the four orientations, the openings that receive the fasteners in the housing 102 and in the pump housing 96 are aligned, allowing the fasteners to be inserted therein and the crankcase 100 to be secured to the pump 28 in the selected orientation.

[0025] With reference to Fig. 8-10, the crankshaft 106 is simply supported by the housing 102 (supported at both ends but freely rotatable). This increases the rigidity and durability of the crankshaft 106 compared to cantilevered crankshaft designs. The crank assembly 104 includes two crankshaft bearings 136 configured to allow the crankshaft 106 to rotate relative to the housing 102. In the illustrated embodiment, the crankshaft 106 rotates about the axis of rotation AR, which is defined by the engine output shaft 86. However, it should be understood that in other configurations, the crankshaft may rotate about other axes of rotation. Each crankshaft bearing 136 supports one of the drive and idler pulleys 112, 114. One crankshaft bearing 136 is disposed between the drive pulley 112 and the housing 102, and the other crankshaft bearing is disposed between the idler pulley 114 and the housing.In the illustrated embodiment, each crankshaft bearing 136 is secured to the corresponding drive pulley 112 or idler pulley 114 (e.g., by an interference fit). The housing 102 includes two bearing supports 138 (. Fig. 10) in the interior of the housing, which are configured to support the two crankshaft bearings 136. In the illustrated embodiment, the two bearing supports 138 have arcuate surfaces that are sized and shaped to match the outer shape of the crankshaft bearings 136. When the crank assembly 104 is installed in the housing 102, each crankshaft bearing 136 rests on one of the bearing supports 138. The crankcase 100 may include a plain bearing bushing or a retainer 140 ( Fig. 9) that secures the crankshaft bearings 136 in the housing 102. The plain bearing bush 140 is releasably connected to the housing 102 by one or more fastening means.

[0026] Preferably, the crankshaft bearings 136 each comprise a sealed bearing. Similarly, the bearings 124 for the connecting rod 110 each preferably comprise a sealed bearing. Additionally, the cylinder liner 130 preferably comprises an impregnated bushing. The use of sealed bearings and the impregnated bushing eliminates, unlike conventional designs, the need to fill the interior of the housing 102 of the crankcase 100 with lubricant, such as from the reservoir 12. In other words, the interior of the housing 102 of the crankcase 100 remains dry. This eliminates the need for the crankcase 100 to have high-pressure seals, thereby reducing maintenance and the risk of oil leaks compared to crankcases filled with lubricant.

[0027] It is understood that other configurations of the crank assembly, such as other ways of converting rotary motion into linear motion, are also within the scope of the present disclosure.

[0028] The crankcase 100 of the present disclosure is configured for easy installation of the crank assembly 104 into the housing 102 and easy removal of the crank assembly 104 from the housing 102. The crank assembly 104 is at least one of installable into the housing 102 or removable from the housing 102 without having to disassemble the crank assembly. In the illustrated embodiment, the crank assembly 104 is both installable into the housing 102 and removable from the housing 102 without having to disassemble the crank assembly. In other words, the crank assembly 104 may be in a fully assembled configuration - the crankshaft 106 is assembled with the connecting rod 110 and the crankshaft bearings 136 mounted thereon, and the connecting rod is mounted to the piston 108 (as in Fig. 9) - before being installed in the housing 102. This allows for faster and easier assembly of the crankcase 100 and easier disassembly of the crankcase, such as for maintenance or component replacement, compared to conventional crankcases in which final assembly of a crank assembly occurs within the crankcase, such as by inserting a shaft through one or more components. The housing 102 of the crankcase 100 allows the fully assembled crank assembly 104 to be easily inserted into and removed from the housing without having to separate components of the crank assembly. The housing 102 includes an access opening 142.The crank assembly 104 is arranged relative to the housing 102 and the access opening 142 such that the crank assembly can be inserted into and removed from the housing through the access opening without disassembling the crank assembly. More specifically, the crank assembly 104 is arranged relative to the housing 102 and the access opening 142 such that the crank assembly can be inserted into and removed from the housing through the access opening without separating the crankshaft 106, the piston 108, and the connecting rod 110. The access opening 142 is sized, shaped, and arranged relative to the crank assembly 104 (when the crank assembly is arranged within the interior of the housing 102) such that the crank assembly, in a fully assembled configuration, can be removed from the housing through the access opening.Likewise, in the fully assembled configuration, the crank assembly 104 is insertable into the housing 102 through the access opening 142. The access opening 142 has a length L that is greater than a corresponding length of the crank assembly 104 and a width W that is greater than a corresponding width of the crank assembly. Furthermore, the interior of the housing 104 is sized and shaped to allow the piston 108 to move freely from the access opening 142 into the liner 130 and vice versa.

[0029] The access opening 142 is oriented relative to the rotation axis AR such that the crank assembly 104 is insertable into and removable from the enclosure 102 through the access opening along an installation axis IA that is non-parallel to the rotation axis. In the illustrated embodiment, the access opening 142 is disposed at the top of the enclosure 102 such that the installation axis IA is generally vertical, allowing the crank assembly 104 to be lowered downward into the enclosure and lifted upward out of the enclosure. Thus, in the illustrated embodiment, the installation axis IA is generally normal to the rotation axis AR. The installation axis IA is also generally parallel or coextensive with the piston axis PA and normal to a plane defined by the access opening 142.The access opening 142 may also be arranged at other locations in the housing 102, and / or the installation axis IA may also extend in other orientations relative to the rotation axis AR. The crankcase 100 includes a cover 144 configured to close the access opening 142. One or more fasteners releasably attach the cover 144 to the housing 142, thereby closing the access opening 142.

[0030] The installation and removal of the crank assembly 104 into and from the housing 102 of the crankcase 100 will now be described. To install the crank assembly 104, the crank assembly is first assembled. This includes assembling the crankshaft 106, coupling the connecting rod 110 to the crankshaft, coupling the connecting rod to the piston 108, and mounting the crankshaft bearings 136 on the crankshaft. After the crank assembly 104 is assembled, the crank assembly is aligned with the access opening 142 and then moved along the installation axis 1A into the interior of the housing 102. If necessary, the cover 144 is separated from the housing 102 to open the access opening. The crank assembly 104 is moved along the installation axis IA until the crankshaft bearings 136 engage and rest on the bearing supports 138 of the housing 102.As the crank assembly 104 is moved along the installation axis IA, the piston 108 moves toward and into the bushing 130. The journal bearing bushing 140 is then inserted through the access opening 142 along the installation axis IA, engaged with the crankshaft bearings 136, and then secured to the housing 102 with one or more fasteners. The cover 144 is then attached to the housing 102. The motor 26 can then be attached to the crankcase 100 by sliding the output shaft 86 along the rotational axis AR into the motor connector 120 of the drive pulley 112 and then securing the motor to the housing 102 with one or more fasteners. These steps are generally reversed to remove the crank assembly 104 from the housing 102 of the crankcase 100.First, the motor 26 is separated from the housing 102, and the output shaft 86 is separated from the drive pulley 112 by sliding the output shaft away from the drive pulley along the rotational axis AR. The cover 144 is separated from the housing 102 to open the access opening 142. Thereafter, the plain bearing bushing 140 is separated from the housing 102 and removed from the interior of the housing through the access opening 142. Next, the crank assembly 104 is moved along the installation axis IA toward the access opening 142. During this movement, the piston 108 slides out of the bushing 130. The crank assembly 104 is moved out of the interior of the housing 102 through the access opening 142 to complete the removal of the crank assembly 104.

[0031] The motor 26 is mounted directly to the housing 102 of the crankcase 100 by one or more fasteners. In one embodiment, the motor 26 comprises an electric motor, as shown in the Fig. 3, Fig. 4, Fig. 6, Fig. 8 and Fig. 9. In one embodiment, the motor comprises a hydraulic motor 26' as shown in Fig. 7. The electric motor 26 and the hydraulic motor 26' are interchangeable. For example, the pump assembly 14 includes a motor connector 103 configured to operatively couple a motor to the pump 28. In this embodiment, the housing 102 of the crankcase 100 forms the motor connector 103. In the illustrated embodiment, the motor connector 103 includes one or more threaded openings for receiving fasteners (e.g., bolts) that secure the motor to the motor connector, although other types of motor connectors may be used without departing from the scope of the present disclosure. The motor connector 103 may connect the electric motor 26 or the hydraulic motor 26' to the crankcase 100. In one embodiment, the lubricant distribution system 10 includes a set of motors, the set including the electric motor 26 and the hydraulic motor 26'.The electric motor 26 includes a connector 27, and the hydraulic motor 26' includes a connector 27'. Both connectors 27, 27' are configured to be connected to the motor connector to interchangeably couple the respective electric motor 26 and hydraulic motor 27' to the pump. In the illustrated embodiment, the connectors 27, 27' include openings aligned with the threaded openings in the motor connector 103 to allow the insertion of fasteners therethrough.

[0032] With reference to Fig. 1, Fig. 2 and Fig. 11, the pump 28 comprises a pump supply outlet 90 ( Fig. 11), a pump feed inlet 92 ( Fig. 1 and Fig. 2) and a pump supply passage 94 ( Fig. 2) that provides fluid communication between the pump supply outlet and the pump supply inlet. The pump supply passage 94 extends along the lance structure 32 of the pump. The pump 28 is configured to pump the lubricant from the reservoir 12 through the pump supply outlet 90. The lubricant in the reservoir 12 flows through the pump supply inlet 92, through the pump supply channel 94, and out the pump supply outlet 90. In this manner, the pump supply inlet 92 can also be considered a reservoir supply outlet through which lubricant flows out of the reservoir interior 22. In the illustrated embodiment, the pump supply inlet 92 includes one or more openings and / or an open lower end of the pump supply passage 94. Other configurations of the pump supply inlet 92 are also within the scope of the present disclosure.The pump supply outlet 90 and the pump refill inlet 36 are each defined by the pump housing 96 and are located above the lid 20 of the reservoir 12.

[0033] With reference to Fig. 1, Fig. 3, and Fig. 4 and on Fig. 12-18, the lubricant distribution system 10 includes a valve assembly 200. The valve assembly 200 includes a mounting bracket (e.g., a mounting block) 202 and one or more valves coupled to the mounting bracket. In the illustrated embodiment, the valve assembly 200 includes a one-way valve 204, a vent valve 206, and a pressure relief valve 208. In other embodiments, the valve assembly need only include one or two (in any combination) of the one-way valve 204, the vent valve 206, or the pressure relief valve 208 coupled to the mounting bracket. The mounting bracket 202 fluidly couples the one-way valve 204, the vent valve 206, and the pressure relief valve 208. In conventional systems, the one or more valves would be connected to each other with hoses, resulting in a complicated piping system.The mounting bracket 202 eliminates the need for such hoses and simplifies the design of the lubricant distribution system.

[0034] With reference to Fig. 12-18, the mounting bracket 202 includes a mounting bracket body 210. Preferably, the mounting bracket body 210 is, as illustrated, a single unitary piece of material. In other embodiments, the mounting bracket body may be formed from multiple pieces joined together, for example, by welding or fasteners. The mounting bracket body 210 may be formed from any suitable material capable of withstanding the pressure of the lubricant, such as metal (aluminum). The mounting bracket body 210 includes a one-way valve port 218. The one-way valve port 218 is configured to removably couple the one-way valve 204 to the mounting bracket body 210. The one-way valve port 218 includes a one-way valve chamber 218A sized and shaped to receive at least a portion of the one-way valve 204.In one embodiment, the one-way valve 204 is threadably coupled to the one-way valve port 218 (the one-way valve has an external thread that threads with the internal thread of the one-way valve port), although other ways of connecting the one-way valve to the one-way valve port are within the scope of the present disclosure. The mounting bracket body 210 includes a vent valve port 220. The vent valve port 220 is configured to removably couple the vent valve 206 to the mounting bracket body 210. The vent valve port 220 includes a vent valve chamber 220A sized and shaped to receive at least a portion of the vent valve 206.In one embodiment, the vent valve 206 is threadably coupled to the vent valve port 220 (the vent valve has an external thread that threads with the internal thread of the vent valve port), although other ways of connecting the vent valve to the vent valve port are within the scope of the present disclosure. The mounting bracket body 210 includes a pressure relief valve port 222. The pressure relief valve port 222 is configured to removably couple the pressure relief valve 208 to the mounting body 210. The pressure relief valve port 222 includes a pressure relief valve chamber 222A sized and shaped to receive at least a portion of the pressure relief valve 208.In one embodiment, the pressure relief valve 208 is threadably coupled to the pressure relief valve port 222 (the pressure relief valve has an external thread that threads into the internal thread of the pressure relief valve port), although other ways of connecting the pressure relief valve to the pressure relief valve port are also within the scope of the present disclosure. Chambers 218A, 220A, 222A may each include a blind bore.

[0035] The mounting bracket body 210 has a mounting bracket inlet 212. The mounting bracket inlet 212 is configured to receive the lubricant from the pump 28. The mounting bracket body 210 has a mounting bracket outlet 214 (in the broadest sense, at least one mounting bracket outlet). The mounting bracket outlet 214 is in fluid communication with the mounting bracket inlet 212. The mounting bracket outlet 214 is configured to supply lubricant. More specifically, the mounting bracket outlet 214 is configured to be coupled to a single supply line (not shown) of the overall lubrication system to transport the lubricant moved by the pump toward the one or more injectors. In this way, the mounting bracket outlet 214 can be considered a lubricant outlet of the lubricant distribution system 10.In the illustrated embodiment, the mounting bracket body 210 includes two mounting bracket outlets 214. The two mounting bracket outlets 214 are located on opposite sides of the mounting bracket body 210. In operation, each mounting bracket outlet 214 can be attached to a corresponding individual supply line, or one mounting bracket outlet 214 can be attached to an individual supply line and the other mounting bracket outlet can be blocked with a plug (not shown).

[0036] The mounting bracket body 210 includes a mounting bracket supply passage 216 fluidly connecting the mounting bracket inlet 212 and the mounting bracket outlet 214. The one-way valve port 218 is fluidly disposed between the mounting bracket inlet 212 and the mounting bracket outlet 214. The mounting bracket supply passage 216 includes a first supply section 216A extending from the mounting bracket inlet 214 to the one-way valve chamber 218A (the one-way valve chamber may be considered part of the mounting bracket supply passage) and a second supply section 216B extending from the one-way valve chamber and the two mounting bracket outlets 214. In the illustrated embodiment, the second supply section 216B includes a through-bore through the mounting bracket body 210 that intersects the one-way valve chamber 218, with the opposite ends of the through-bore forming the two mounting bracket outlets.

[0037] The mounting bracket body 210 may also include an air vent outlet 224. The air vent outlet 224 is configured to vent air (including lubricant with entrained air) that becomes trapped in the conduit system (e.g., in the pump supply passage 94) of the lubricant distribution system 10. The air vent outlet 224 is in fluid communication with the mounting bracket inlet 212. In particular, the air vent outlet 224 is in fluid communication with the mounting bracket inlet 212 without an intervening component, such as a valve (e.g., a one-way valve 204), fluidly disposed therebetween. In the illustrated embodiment, the mounting bracket body 210 includes an air vent passage 226 that fluidly connects the air vent outlet 224 to the mounting bracket inlet 212.In the illustrated embodiment, the air vent passage 226 extends from the one-way valve chamber 218A from a location upstream of the one-way valve 204 to the air vent outlet 224. The valve assembly 200 includes an air vent plug 228 for selectively opening and closing the air vent outlet 224. For example, the air vent plug 228 may be threadably coupled to the mounting bracket body 210. Typically, the air vent plug 228 is coupled to the mounting body 210 to close the air vent outlet 224. When desired, the air vent plug 228 is separated from the mounting body 210 to open the air vent outlet 224 to purge air, such as when a user primes the pump 28.

[0038] The mounting bracket body 210 includes a mounting bracket refill inlet 230. The mounting bracket refill inlet 230 is configured to receive the lubricant from the lubricant supply. More specifically, the mounting bracket refill inlet 230 receives the lubricant from the lubricant supply after the lubricant has flowed through the isolation valve 40. The mounting bracket refill inlet 230 is in fluid communication with the isolation valve outlet 46. In the illustrated embodiment, the mounting bracket refill inlet 230 is connected to (broadly configured to be connected to) the refill line 50 extending between the isolation valve 40 and the mounting bracket body 210.The mounting bracket body 210 includes a mounting bracket refill outlet 232 (for reasons that will become apparent, the mounting bracket refill outlet may also be considered a mounting bracket return outlet). The mounting bracket refill outlet 232 is configured to supply lubricant to the reservoir 12 via the reservoir refill inlet 34. The mounting bracket refill outlet 232 is in fluid communication with the mounting bracket refill inlet 230. The mounting bracket body 210 includes a mounting bracket refill passage 234 that fluidly connects the mounting bracket refill outlet 232 to the mounting bracket refill inlet 230 (without any intervening components). Thus, lubricant from the lubricant supply from the shut-off valve 40 flows into the mounting bracket refill inlet 230, through the mounting bracket refill passage 234, and out the mounting bracket refill outlet 232.

[0039] The mounting bracket refill outlet 232 is in fluid communication with each of the mounting bracket outlets 214. The vent valve port 220 is fluidly disposed between the mounting bracket refill outlet 232 and the mounting bracket outlets 214. The mounting bracket body 210 has a vent passage 236 that fluidly connects the vent valve port 220 to the mounting bracket outlets 214. In the illustrated embodiment, the vent passage 236 extends from the second supply section 216A to the vent valve chamber 220A ( Fig. 16). The vent valve chamber 220A is intersected by the mounting bracket refill passage 234 (the vent valve chamber can be considered part of the vent passage). Thus, each mounting bracket outlet 214 is fluidly connected via the vent valve port 220 to the mounting bracket refill outlet 232 ( Fig. 15). The mounting bracket outlets 214 are each in fluid communication with the pressure relief port 222. The mounting bracket body 210 has a pressure relief passage 238 that fluidly connects the pressure relief port 222 to the mounting bracket outlets 214. In the illustrated embodiment, the pressure relief passage 238 extends from the second supply section 216A to the pressure relief valve chamber 222A ( Fig. 14) (the pressure relief chamber may be considered part of the pressure relief passage). The pressure relief port 222 and the vent valve port 220 are each located downstream of the one-way valve port 218.

[0040] With reference to Fig. 1-4 and 11-18, the valve assembly 200 in the assembled lubricant distribution system 10 is mounted directly to the pump 28. The mounting bracket 202 (more precisely, the mounting bracket body 210) is mounted directly to the pump 28. For example, one or more fasteners may attach the mounting bracket body 210 to the pump housing 96 of the pump 28. The mounting bracket inlet 212 is in fluid communication with the pump supply outlet 90. The mounting bracket refill outlet 232 is in fluid communication with the pump refill inlet 36. Thus, the mounting bracket refill outlet 232 is in fluid communication with the reservoir refill inlet 34. Seals 240 ( Fig. 11), such as O-rings, may be disposed between the mounting bracket 202 and the pump housing 96 to seal the flow connection between the mounting bracket inlet 212 and the pump supply outlet 90, and the flow connection between the mounting bracket refill outlet 232 and the pump refill inlet 36. After assembly, the lubricant pumped by the pump 28 flows from the pump supply outlet 90 into the mounting bracket inlet 212, through the mounting bracket supply passage 216, and out one or both of the mounting bracket outlets 214. Furthermore, the lubricant from the lubricant supply from the isolation valve 40 flows into the mounting bracket refill inlet 230, through the mounting bracket refill passage 234, through the mounting bracket refill outlet 232, and toward the reservoir refill inlet 34.

[0041] In the assembled lubricant distribution system 10, the one-way valve 204 is removably coupled to the one-way valve port 218. Accordingly, the one-way valve 204 is fluidly disposed between the mounting bracket inlet 212 and each of the mounting bracket outlets 214. The one-way valve is configured to permit the flow of lubricant from the mounting bracket inlet 212 to each of the mounting bracket outlets 214 and to prevent the flow of lubricant from the mounting bracket outlets to the mounting bracket inlet. Disposing the one-way valve 204 upstream of the two mounting bracket outlets 214 (broadly defined, at least one mounting bracket outlet) eliminates the need for the lubricant distribution system 10 to have multiple one-way valves. Conventional systems typically include a one-way valve for each outlet connected to a single supply line.In the illustrated embodiment, the one-way valve 204 comprises a check valve, such as a double check valve, although the use of other types of one-way valves is also within the scope of the present disclosure. The one-way valve 204 includes an inlet at the bottom and an outlet located above the inlet along the side of the one-way valve. The one-way valve port 218 is sized and shaped to provide a clearance between the inlet and the bottom of the one-way valve chamber 218A and a clearance between the outlet and the side of the one-way valve chamber to allow lubricant to flow from the first supply section 216A into a lower portion of the one-way valve chamber, into the one-way valve inlet, out the one-way valve outlet into an upper portion of the one-way valve chamber, and into the second supply section 216B.The one-way valve 204 creates a seal with the one-way valve port 218 via a sealing element that defines and separates the lower and upper portions of the one-way valve chamber.

[0042] The vent valve 206 is removably coupled to the vent valve port 220. Accordingly, the vent valve 206 is fluidly disposed between each mounting bracket outlet 214 and the mounting bracket refill outlet 232. The vent valve 206 is configured to relieve lubricant pressure at the mounting bracket outlets 214. Relieving the lubricant pressure generated by the pump 28 at the mounting bracket outlets 214 relieves the lubricant pressure within the individual supply lines and at the one or more injectors, allowing the injectors to reset to deliver the next dose of lubricant. The vent valve 206 is configured to selectively permit the flow of lubricant toward the reservoir 12 via the mounting bracket refill outlet 232 and the reservoir refill inlet 34 to relieve lubricant pressure at the mounting bracket outlets 214.When closed, the vent valve 206 prevents the flow of lubricant from the mounting bracket outlets 214 toward the mounting bracket refill outlet 232. When open, the vent valve 206 allows the flow of lubricant from the mounting bracket outlets 214 toward the mounting bracket refill outlet 232. Thus, the vented lubricant is directed back into the interior 22 of the reservoir 12. The vent valve 206 may comprise an electrically operated vent valve or a hydraulically operated vent valve. Thus, the vent valve port 220 is configured to be interchangeably coupled to an electrically operated vent valve and a hydraulically operated vent valve.Typically, the lubricant distribution system 10 includes the electrically operated vent valve when the motor 26 is an electric motor and the hydraulically operated vent valve when the motor is a hydraulic motor 26'. However, it should be understood that the lubricant distribution system 10 may also include the electrically operated vent valve when the motor is a hydraulic motor 26' and the hydraulically operated vent valve when the motor is an electric motor 26. In the embodiments shown in FIG. Fig. 1, Fig. 3 and Fig. 4 and in Fig. 12-18, the vent valve 206 includes the electrically actuated vent valve. The electrically actuated vent valve 206 includes a connector (e.g., a port connector) 207 configured to couple to the vent valve port 220. In one embodiment, the connector 207 includes a thread (e.g., an external thread) to threadably couple the electrically actuated vent valve 206 to the vent valve port 220, although other ways of connecting the electrically actuated vent valve to the vent valve port may be used without departing from the scope of the present disclosure. The electrically actuated vent valve 206 includes an inlet 209 and an outlet 211 fluidly coupled to the inlet.In the illustrated embodiment, inlet 209 includes a plurality of openings circumferentially spaced around vent valve 206. Connector 207 is configured such that, when the connector is connected to vent valve port 220, inlet 209 is positioned to receive lubricant downstream of mounting bracket outlet 214, and outlet 211 is positioned to discharge lubricant toward mounting bracket return outlet 232. In the illustrated embodiment, inlet 209 is positioned in vent valve chamber 220A and receives lubricant from the vent valve chamber. Outlet 211 is positioned either at the bottom of vent valve chamber 220A or in mounting bracket refill passage 234 and is configured to direct lubricant into the mounting bracket refill passage.Electrically actuated vent valves are known to those skilled in the art, and therefore a more detailed description is omitted here. Further details regarding a hydraulically actuated vent valve suitable for use with the lubricant distribution system 10 of the present disclosure are set forth below.

[0043] The pressure relief valve 208 is removably coupled to the pressure relief valve port 222. Accordingly, the pressure relief valve 208 is in fluid communication with the mounting bracket outlets 214. The pressure relief valve 208 is configured to relieve the lubricant pressure at the mounting bracket outlets 214 when the lubricant pressure exceeds a threshold pressure. The threshold pressure is greater than the pressure required by the injectors to deliver lubricant. Injectors typically operate with a lubricant pressure within a range of about 2,500 psi to about 3,500 psi. In one embodiment, the threshold pressure for the pressure relief valve 208 is about 4,000 psi. As mentioned above, relieving the lubricant pressure at the mounting bracket outlets 214 relieves the lubricant pressure within the individual supply lines and at the one or more injectors.Relieving the lubricant pressure via the pressure relief valve 208 prevents the pump 28 from overpressurizing the lubricant in the lubrication system (e.g., in the mounting bracket 202, in the individual supply lines, etc.) and damaging the lubrication system components. In the illustrated embodiment, the pressure relief valve 208 is configured to vent the lubricant to the atmosphere.

[0044] The valve assembly 200 of the present disclosure allows the one-way valve 204, the vent valve 206, and the pressure relief valve 208 to be serviced, replaced, or cleaned without having to disconnect other components (such as the pump 28, the individual supply lines, or other hoses or fittings) of the lubrication system. This reduces the risk of contamination or error and shortens maintenance time. For example, conventional lubrication systems include an inline check valve that requires an operator to loosen two hose fittings to disconnect and remove the check valve from the system.

[0045] The operation of the valve assembly 200 will now be described. As the pump 28 pumps the lubricant from the reservoir 12, the lubricant flows into the mounting bracket inlet 212, along the mounting bracket supply passage 216, and through the one-way valve 204 and through the mounting bracket outlets 214 into the individual supply lines coupled thereto. During this operation, the vent valve 208 is closed. The one-way valve 204 prevents the lubricant from flowing back into the reservoir 12 via the mounting bracket inlet 212. The pump 28 continues to pump the lubricant to build pressure in the individual supply lines to activate the injectors. After the injectors have delivered the lubricant, the vent valve 206 is opened (and the pump 28 stops).This allows lubricant to flow from the mounting bracket outlets 214 along the mounting bracket refill passage 234 and through the vent valve 208, through the mounting bracket refill outlet 232, and toward the reservoir refill inlet 34 (via the pump refill inlet 36 and the pump refill passage 38) to flow back into the reservoir 12. Allowing lubricant to flow through the vent valve 208 reduces the lubricant pressure, thereby allowing the injectors to reset. When the vent valve 208 is open, the pump 28 stops operating. If the downstream pressure of the one-way valve 204 (such as at the mounting bracket outlets 214, in the individual supply lines, or at the injectors) exceeds the threshold pressure, the pressure relief valve 208 opens to allow the flow of lubricant therethrough to reduce the pressure.For example, the lubricant pressure may exceed the threshold pressure if a lubricant blockage forms.

[0046] With reference to Fig. 19-21B, a vent valve according to an embodiment of the present disclosure is generally designated by reference numeral 300. As shown in Fig. 19, the vent valve 300 is usable with the mounting bracket 202 to serve as the vent valve for the lubricant distribution system 10 of the present disclosure. In other words, the vent valve 300 of the Fig. 19-21B may be the vent valve 206 described above. The vent valve 300 is a hydraulically actuated vent valve. Vent valves come in various types, such as (1) pneumatic, (2) hydraulic, (3) electric, and (4) mechanical. Each type of vent valve operates according to its own mechanism, which differs from the other types. For example, electrically actuated vent valves energize a solenoid to open and / or close the valve. Hydraulically actuated vent valves use a pressurized piston to hold the valve closed. The various types of vent valves have different configurations and arrangements that are incompatible with each other. Therefore, it is not possible to simply interchange one type of conventional vent valve with another type of vent valve.Unlike these conventional vent valves, the hydraulically actuated vent valve 300 of the present disclosure and an electrically actuated vent valve are interchangeable, such as the vent valve 206 shown in FIG. Fig. 1, Fig. 3 and Fig. 4 and in the Fig. 12-18. Both the electrically actuated vent valve 206 and the hydraulically actuated vent valve 300 are connectable to the vent valve port 220 of the mounting bracket 202 without having to modify, reconfigure, or otherwise alter the mounting bracket to be used with the respective vent valve design.

[0047] The vent valve 300 includes a valve housing 302 and a blocker 304. The blocker 304 is supported by the enclosure 302. The blocker 304 is movably disposed within the enclosure 302. The enclosure 302 has an interior space including a chamber 306 and a longitudinal bore 308 extending from the chamber. In the illustrated embodiment, the blocker 304 includes a piston having a head 310 disposed within the chamber 306 and a slide rod or stem 312 disposed within the bore 308. The bore 308 defines a valve axis VA along which the head 310 and slide rod 312 of the blocker 304 move. A hydraulic port 314 is disposed at one end of the chamber 306. The hydraulic port 314 is configured to be connected to a hydraulic line (not shown). Together, the hydraulic port 314 and the head 310 define a pressure section 306A of the chamber 306.During operation, the pressure section 306A is filled and pressurized with a fluid (such as hydraulic fluid) from the hydraulic line connected to the hydraulic port 314. This expands the pressure section 306A by forcing the blocker 304 (more precisely, the head 310) to move along the valve axis VA from the position shown in . Fig. 21A shown position into the Fig. 21B to close the vent valve 300. In one embodiment, the pressure section 306A can be pressurized to within a range of approximately 350-400 psi to move the blocker 304 to the closed position and maintain the blocker in the closed position. The head 310 includes a first sealing member 316 that forms a seal with the inner surface of the housing 302 defining the chamber 306. The housing 302 also includes a second sealing member 332 that forms a seal with the slide rod 312.

[0048] The housing 302 includes an insertion portion 302A sized and shaped to be inserted into the vent valve chamber 220A of the vent valve port 220 of the mounting bracket 202. The insertion portion 302A includes a connector (e.g., a port connector) 307 configured to couple to the vent valve port 220 of the mounting bracket 202. In one embodiment, the connector 307 includes a thread (e.g., an external thread) to threadably couple the hydraulically actuated vent valve 300 to the vent valve port 220, although other ways of connecting the hydraulically actuated vent valve to the vent valve port may be used without departing from the scope of the present disclosure.The insertion portion 302A (generally the enclosure 302) includes a first opening 318, a second opening 320, and a valve passage 322 providing fluid communication between the first and second openings. In the illustrated embodiment, the first opening 318 includes a plurality of openings circumferentially spaced around the insertion portion 302A. The vent valve 300 is a bidirectional vent valve, meaning that the vent valve can vent in two directions: a first flow direction from the first opening 318 toward the second opening 320, and a second flow direction (generally opposite the first flow direction) from the second opening toward the first opening. Accordingly, the first opening 318 can be considered an inlet, and the second opening 320 can be considered an outlet when the vent valve 300 is venting in the first flow direction.Likewise, when the vent valve 300 vents in the second flow direction, the first port 318 may be considered an outlet, and the second port 320 may be considered an inlet. Conventional hydraulic vent valves can only vent in a single direction. When used in the lubricant distribution system 10 of the present disclosure, the vent valve 300 vents in the first flow direction. However, in other contexts, including other lubricant distribution systems, the vent valve 300 may also vent in the second flow direction.

[0049] The first opening 318 faces in a first direction, and the second opening faces in a second direction different from the first direction. In one embodiment, the first and second directions are non-parallel to each other. In the illustrated embodiment, the first and second directions are generally perpendicular to each other. The first direction is generally perpendicular or laterally outward relative to the valve axis VA, and the second direction is generally parallel to the valve axis. In the illustrated embodiment, the first opening 318 is arranged to allow lubricant to move into or out of one side of the housing 302. The second opening 320 is arranged to allow lubricant to move into or out of one end (such as a bottom end) of the housing 302.Other configurations and arrangements of the first and second openings are also within the scope of the present disclosure. With respect to use with the mounting bracket 202 of the present disclosure, the connector 307 is configured such that, when the connector is coupled to the vent valve port 220, the first opening 318 (e.g., the inlet) is arranged to receive lubricant downstream of the mounting bracket outlet 214, and the second opening 320 (e.g., the outlet) is arranged to discharge lubricant toward the mounting bracket return outlet 232. The arrangement or positioning of the first opening 318 and the second opening 320 of the hydraulically actuated vent valve 300 relative to the vent valve port 220 is substantially similar (if not identical) to the arrangement or positioning of the inlet 209 and the outlet 214, respectively.of the outlet 211 of the electrically actuated vent valve 206 relative to the vent valve port. For example, the first opening 318 is located in the vent valve chamber 220A and receives lubricant from the vent valve chamber. The second opening 320 is located either at the bottom of the vent valve chamber 220A or in the mounting bracket refill passage 234 and is configured to direct the lubricant into the mounting bracket refill passage.

[0050] The vent valve 300 has a valve seat 324. The valve seat 324 is supported by the housing 302. In particular, the valve seat 324 is attached to the insertion portion 302A of the housing 302. The valve seat 324 is arranged in the valve passage 322 between the first and second openings 318, 320. The blocker 304 is movable relative to the valve seat 324 between an open position ( Fig. 21A) and a closed position ( Fig.21B). In the open position, the blocker 304 allows the flow of lubricant between the first and second openings 318, 320. The blocker 304 is spaced from the valve seat 324, thereby allowing the lubricant to flow therebetween. In the closed position, the blocker 304 engages the valve seat 324 to block the flow of lubricant between the first and second openings 318, 320. The blocker 304, or more specifically, the slide rod 312, has a conical portion 328 configured to engage the valve seal 324. The conical portion 328 has a blocker sealing surface 330. The valve seat 324 has a corresponding seat sealing surface 326. The blocker sealing surface 330 engages the seat sealing surface 326 to close the vent valve 300.The blocker sealing surface 330 and the seat sealing surface 326 each have a frustoconical shape or are tapered relative to the valve axis VA. Other configurations of the sealing surfaces are also within the scope of the present disclosure. The seat sealing surface 326 separates a first passage section 322A from a second passage section 322B.

[0051] The blocker 304 is configured to be moved from the closed position toward the open position by the lubricant pressure in the valve passage 322 when the flow of lubricant occurs from the first port toward the second port (in the first flow direction) and when the flow of lubricant occurs from the second port toward the first port (in the second flow direction). This capability enables the vent valve 300 to be bidirectional. To allow the blocker 304 to move from the closed position toward the open position, the pressure section 306A of the pressure chamber 306 is depressurized (to or near 0 psi).Therefore, to move the blocker 304 toward the open position, the net force F acting on the blocker from the pressurized lubricant in the valve passage 322 (along the valve axis VA, and in the direction the blocker moves from the closed position to the open position) must be large enough to overcome any friction to which the blocker is subject (such as due to the seals 316, 332), any residual pressure in the pressure section 306A, and the weight of the blocker. The lubricant pressure in the valve passage 322 required to open the vent valve 300 is generally the same as the pressure required to operate the one or more injectors (approximately 2500-3500 psi).

[0052] When the vent valve 300 vents in the first flow direction (as would be the case if installed in the lubricant distribution system 10 of the present disclosure), the net force F acting on the blocker 304 is a function of the difference in the cross-sectional area of ​​the seal formed between the slide rod 312 and the second sealing element 332 and the cross-sectional area of ​​the seal formed between the slide rod and the valve seat 324. This difference is multiplied by the lubricant pressure in the first passage section 322A to obtain the resulting net force F. The difference in the cross-sectional areas between these two seals must thus be large enough to result in a net force F sufficient to move the blocker 304 toward the open position.The difference in cross-sectional areas is directly related to the diameter D1 of the slide rod 312 and a diameter D2 of the valve seat (more precisely, the smallest diameter of the seat sealing surface 326). The larger the diameter D1 of the slide rod 312 relative to the diameter D2 of the valve seat 324, the greater the difference in cross-sectional areas and the greater the net force F acting to move the blocker 304 toward the open position. Preferably, the diameter D1 of the slide rod 312 is at least 25% larger than the diameter D2 of the valve seat 324, or more preferably, at least 40% larger, or most preferably, at least 50% larger. In one embodiment, the diameter D1 of the slide rod 312 is about 0.27555 inches, and the diameter D2 of the valve seat 324 is about 0.1875 inches, corresponding to a difference in cross-sectional areas of about 0.032 inches. 2resulting in a net force F of approximately 112 pounds (when the lubricant pressure in the first passage section 322A is 3,500 psi) acting on the blocker 324 to move the blocker toward the open position, although other configurations may be used without departing from the scope of the present disclosure. In this embodiment, the diameter D1 of the slide rod 312 is approximately 47% larger than the diameter D2 of the valve seat 324. Another way to express the desired relative sizes of the slide rod 312 and the valve seat 324 may be in terms of the relative sizes of the cross-sectional areas. For example, in one embodiment, the difference in the cross-sectional areas of the seals is approximately equal to, or greater than, the cross-sectional area of ​​the seal formed between the slide rod 312 and the valve seat 324.This results in the net force F when the vent valve 300 vents in the first flow direction being approximately equal to, or greater than, the net force when the vent valve vents in the second flow direction (described below) (and when the lubricant pressure is the same). Furthermore, to ensure that the pressure in the pressure section 306A can maintain the blocker 324 in the closed position even when the first passage section 322A is pressurized with lubricant, the cross-sectional area of ​​the head 310 (more precisely, the cross-sectional area of ​​the seal formed between the head and the first sealing element 316) is preferably at least 10 times larger, or more preferably at least 15 times larger, than the difference in cross-sectional areas.This allows the pressure in the pressure section 306A to be much lower than the pressure in the first passage section 332A while still allowing the blocker 324 to be held in the closed position.

[0053] When the vent valve 300 vents in the second flow direction, the net force F acting on the blocker 304 is a function of the cross-sectional area of ​​the seal formed between the slide rod 312 and the valve seat 324. This difference is multiplied by the lubricant pressure in the second passage section 322B to obtain the resulting net force F. The cross-sectional area of ​​this seal must therefore be large enough to produce a net force F sufficient to move the blocker 304 toward the open position. The cross-sectional area is directly related to the diameter D2 of the valve seat 324 (more precisely, the smallest diameter of the seat seal surface 326). In the embodiment described above, where the diameter D2 of the valve seat 324 is about 0.1875 inches (a cross-sectional area of ​​about 0.02761 in 2), the resulting net force F is approximately 97 pounds (when the lubricant pressure in the second passage section 322B is 3,500 psi) acting on the blocker 324 to move the blocker toward the open position.

[0054] Because the blocker 304 is moved toward the open position by the lubricant pressure in the valve passage (regardless of whether the flow of lubricant occurs in the first flow direction or the second flow direction), the vent valve 300 does not require an opening mechanism, such as a spring, a solenoid, etc., to move the blocker toward the open position. However, an opening mechanism may be used without departing from the scope of the present disclosure.

[0055] In one embodiment, a valve set is provided for the lubricant distribution system 10. The valve set may include the mounting bracket 202, the electrically actuated vent valve 206, and the hydraulically actuated vent valve 300. The electrically actuated vent valve 206 and the hydraulically actuated vent valve 300 are interchangeably coupled to the vent valve port 220 of the mounting bracket 202. The electrically actuated vent valve 206 and the hydraulically actuated vent valve 300 are each configured to allow lubricant to be vented from the mounting bracket outlet 214 toward the mounting bracket refill outlet 232 when coupled to the vent valve port 220.To enable the mutual interchangeability of the electrically actuated vent valve 206 and the hydraulically actuated vent valve 300 with the vent valve port 220, each of the respective connectors 207, 307 has the same thread (e.g., the same thread size) for screwing onto the vent valve port. Furthermore, since the positioning of the first opening 318 and the second opening 320 of the hydraulically actuated vent valve 300 relative to the vent valve port 220 is substantially similar (if not identical) to the positioning of the inlet 209 and the outlet 211, respectively, of the electrically actuated vent valve 206 relative to the vent valve port, both vent valves are plug-and-play operable with the mounting bracket 202 without requiring any modification or design of the mounting bracket when selecting the type of vent valve to be used.In one embodiment, the lubricant distribution system 10 includes the electrically actuated vent valve 206 coupled to the mounting bracket 202 and the electric motor 26 connected to the motor connector 103. In another embodiment, the lubricant distribution system 10 includes the hydraulically actuated vent valve 300 coupled to the mounting bracket 202 and the hydraulic motor 26' connected to the motor connector 103. In another embodiment, the lubricant distribution system 10 includes the electrically actuated vent valve 206 coupled to the mounting bracket 202 and the hydraulic motor 26' connected to the motor connector 103.

[0056] Having described the disclosure in detail, it will be apparent that modifications and variations are possible without departing from the scope of the disclosure as defined in the appended claims.

[0057] When introducing elements of the present disclosure or its preferred embodiment(s), the articles "a" and "an" are intended to indicate that there are one or more of the elements. The terms "comprising," "containing," and "having" are intended to be inclusive, indicating that there may be additional elements besides those listed.

[0058] In view of the above, it will be seen that the various objects of the disclosure are achieved and other advantageous results are realized.

[0059] Since various changes could be made to the above constructions without departing from the scope of the disclosure, it is intended that all matters contained in the above description and shown in the accompanying drawings be interpreted as illustrative and not in a limiting sense. QUOTES CONTAINED IN THE DESCRIPTION

[0000] This list of documents submitted by the applicant was generated automatically and is included solely for the convenience of the reader. This list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions. Cited patent literature

[0000] US 2,187,684

[0002] US 2,636,441

[0002] US 2,787,225

[0002] US 3,469,532

[0002] US 3,502,029

[0002] US 3,945,772

[0002] US 4,487,340

[0002] US 4,762,474

[0002] US 6,102,676 [0002, 0009] US 9,239,044

[0009]

Claims

[1] Lubricant distribution system comprising: a reservoir configured to contain lubricant, the reservoir comprising a follower plate configured to move up and down within the reservoir in response to a changing lubricant level in the reservoir; a reservoir inlet arranged to supply lubricant to the reservoir; and a shut-off valve in fluid communication with the reservoir inlet, the shut-off valve comprising a blocker selectively positionable to permit lubricant flow through the reservoir inlet and to prevent lubricant flow through the reservoir inlet, the shut-off valve comprising a valve actuator having a follower plate engagement surface arranged to engage the follower plate when the lubricant in the reservoir fills to a predetermined level to position the blocker to prevent lubricant flow through the reservoir inlet, the follower plate engagement surface being movable relative to the blocker. [2] The lubricant distribution system of claim 1, wherein the blocker is configured to move along a blocker axis to selectively permit or prevent lubricant flow through the reservoir inlet, the follower plate engagement surface being movable relative to the blocker along the blocker axis, and the blocker optionally comprising a spool. [3] The lubricant distribution system of claim 1, further comprising a first spring biasing the follower plate engagement surface and the blocker away from each other, and optionally wherein the lubricant distribution system further comprises a second spring biasing the blocker toward a position permitting lubricant flow through the reservoir inlet, and optionally wherein a spring constant of the first spring is greater than a spring constant of the second spring. [4] The lubricant distribution system of claim 1, wherein the valve actuator comprises a spool, the spool being arranged to slide along an axis to engage the blocker to position the blocker to prevent lubricant flow through the reservoir inlet, the spool comprising a first valve stem and a second valve stem movable along the axis relative to the first valve stem, the second valve stem comprising the follower plate engagement surface, and the spool optionally comprising a spring disposed between the first and second valve stems. [5] The lubricant distribution system of claim 1, further comprising a pump configured to pump lubricant from the reservoir. [6] Shut-off valve for lubricant, the shut-off valve comprising: a valve housing having an inlet, an outlet, and a passage fluidly connecting the inlet and the outlet; a blocker selectively positionable relative to the valve body to permit lubricant flow through the passage from the inlet to the outlet, and prevent lubricant flow through the passage from inlet to outlet; and a valve actuator operatively connected to the blocker for selectively positioning the blocker relative to the valve body, the valve actuator having an actuating surface configured to be movable to move the blocker to a position in which the blocker prevents lubricant flow through the passage, the actuating surface being movable relative to the blocker. [7] The shut-off valve of claim 6, wherein the blocker is configured to move along a blocker axis to selectively permit and prevent lubricant flow through the passage, the actuating surface being movable relative to the blocker along the blocker axis, and optionally wherein the valve actuator is configured to move along the blocker axis to selectively position the blocker relative to the valve housing, and optionally wherein the valve actuator comprises a first rod and a second rod, the first and second rods being supported by the valve housing along the blocker axis and being slidable relative thereto along the blocker axis, the first and second rods being slidable relative to each other along the blocker axis, the second rod comprising the actuating surface, and optionally wherein the valve actuator comprises a spring arranged sothat it allows a displacement of the first and second rods relative to each other, wherein the spring is supported by the valve housing and is displaceable relative to it along the blocker axis. [8] The shut-off valve of claim 6, wherein the blocker is configured to move along a blocker axis to selectively permit and prevent lubricant flow through the passage, wherein the actuating surface is movable relative to the blocker along the blocker axis, and wherein the valve actuator comprises a spring arranged to permit movement of the actuating surface relative to the blocker along the blocker axis, and optionally wherein the spring is not compressed when the blocker is in an open position in which the blocker permits lubricant flow through the passage. [9] The shut-off valve of claim 8, wherein the spring is not compressed when the blocker is in a first closed position in which the blocker prevents the flow of lubricant through the passage, and optionally wherein the blocker is movable to a second closed position in which the blocker prevents the flow of lubricant through the passage, the second closed position being different from the first closed position, the blocker being arranged to move in a first direction from the open position through the first closed position to the second closed position, the blocker being prevented from further movement in the first direction when in the second closed position such that movement of the actuating surface in the first direction compresses the spring. [10] The shut-off valve of claim 6, wherein the blocker comprises a coil.

Images